Thermal responsive high pressure butterfly valve seal means



y 1966 w. o. BORCHERDT 3,260,496

THERMAL RESPONSIVE HIGH PRESSURE BUTTERFLY VALVE SEAL MEANS OriginalFiled July 25, 1961 3 Sheets-Sheet 1 fi 1, k 20 10. 4. 05 I50- /103 i/50 ,w 25 35 9 63 T I JI- @woa ICE-1Q 0/ I INVENTOR.

Wan-7e 0. flaw/sear July 12, 1966 w. o. BORCHERDT THERMAL RESPONSIVEHIGH PRESSURE BUTTERFLY VALVE SEAL MEANS Original Filed July 25, 1961 5Sheets-Sheet 2 INVENTOR.

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July 12, 1966 w. o. BORCHERDT THERMAL RESPONSIVE HIGH PRESSURE BUTTERFLYVALVE SEAL MEANS 5 Sheets-Sheet 5 Original Filed July 25, 1961 E N m 4me u T E 8 mm m w 2 r h B \L o m 2 w W 5M||fi fl 2 W F W E H M. -H "M 9United States Patent 3,260,496 THERMAL RESPONSIVE HIGH PRESSUREBUTTERFLY VALVE SEAL MEANS Walter 0. Borclierdt, Mountain Lakes, N.J.,assignor to B. H. Hadley, 1116., Pomona, Calif, a corporation ofCalifornia Original application July 25, 1961, Ser. No. 126,695. Dividedand this application Sept. 16, 1963, Ser. No. 309,074

9 Claims. (Cl. 251-171) This invention relates to a valve means and moreparticularly to a valve means of butterfly type embodying a novelconstruction and mode of operation particularly adaptable for very lowtemperature fluids known as cryogenic fluids. This application is adivisional application of copending application Serial No. 126,695,filed July 25, 1961, now abandoned.

In general, prior proposed butterfly valve devices have included valvediscs pivotal-1y mounted on a disc shaft and arranged in skew relationto a fluid passageway in the valve body. Such skew relation of the valvedisc requires special machining of internal surfaces of the valve bodyin order to provide an effective tight seal. Under conditions of highpressure, the disc shaft was required to be of relatively heavy sectionin order to Withstand such pressures. Since prior proposed disc shaftsextended across the fluid passageway they were subject to bendingstresses. Bearing mountings for such through-disc shafts were likewisespecially constructed to withstand bearing stresses caused by suchloading of the disc shaft in the fluid passageway, all of which tendedto cause non-uniform deflection and relatively rapid bearing wear.

Such prior proposed valve devices having valve discs arranged in skewrelation usually included sealing means at the periphery of the valvedisc wherein the sealing means were carried by the valve body. In othertypes of butterfly valve devices where the valve disc was arrangederpendicular to the fluid passageway or in non-skew relation sealingmeans of prior proposed valve discs were usually carried on theperipheral edge of the valve disc. Tight effective seals were diflicultto achieve under conditions of high fluid pressure. In some instancessuch non-skew valve discs included peripheral sealing means which werecooperable with sealing means provided on the valve body. Such sealingmeans on the valve body required special machining because it will beunderstood that the valve disc is rotated about a diameter and onelialfof the valve disc is moved upstream while the other half is moveddownstream.

The requirement of a zero leakage valve means of butterfly type capableof operating under high fluid pressures and variable fluid temperatureconditions were previously met by prior proposed valves by employingrelatively complicated valve sealing means as mentioned above which wereexpensive, required precision machining of the valve body and were notgenerally suitable or easily and readily operable when low temperaturefluids were held by such prior proposed valve devices.

The present invention contemplates a fluid control valve meansparticularly designed and adapted for use with cryogenic fluids. Thepresent valve construction, while particularly designed for such fluids,is readily adaptable to and capable of utilization with fluids at normaltemperatures or high temperatures. Cryogenic fluids include those havingtemperatures which may extend down to and sometimes below minus 450 F.,such fluids including liquid nitrogen, liquid hydrogen, liquid heliumand liquid oxygen, and the like. The present invention contemplates abutterfly type valve means which is adapted to be useful in storage ofsuch fluids and is movable from closed zero leakage sealed position toan open position wherein substantially full flow of fluid is provided.

The present invention contemplates a valve means of butterfly typewherein a valve body of relatively narrow annular form defines a fluidpassageway, the valve body carrying diametrically disposed stub shafts.A valve member is positioned in said passageway and connected to saidstub shafts. The axis of the valve member is offset with respect to theaxis of the stub shafts and the valve member is provided with aperipheral edge face spaced from the axis of the valve member. Sealmeans provided on the valve body engages in sealing relation theperipheral edge face on the valve member in valve closed position. Invalve open position the spacing of the axes of the valve member and theshaft axis is so arranged that upon rotation of the valve member throughthe seal means is wholly released from its contact with the peripheraledge face of the valve member and is free from any contact with thevalve member. The present invention contemplates a novel seal meansconstruction and a novel construction of the valve member whereby thevalve member may constitute a beam or girder and thereby resist highpressures without imposing severe bendin; stresses on the valve memberor on the stub shafts. The valve means of the present invention alsocontemplates novel bearing means for mounting stub shafts to provide aneffective seal. Actuating means for the valve member includes a novelarrangement [for turning an extension on one of the stub shafts in orderto actuate the valve member.

It is therefore one of the primary objects of the present invention toprovide a butterfly type valve means particularly adapted for use withcryogenic fluids and embodying a novel valve construction adapted foruse with other fluids as well.

An object .of the present invention is to disclose and provide abutterfly type valve means employing a valve member disposed in non-skewrelation to the fluid passageway and constructed as a beam or girder ofuniform thickness.

Another object of the invention is to disclose and provide a butterflytype valve construction wherein the valve member is arranged in nonskewrelation to the fluid passageway and wherein seal means are carried bythe valve body for sealing engagement with the valve member in valveclosed position and free from contact with the valve member in valveopen position.

Still another object of the present invention is to disclose a sealingmeans adapted to be carried by a valve body for engagement with abutterfly type valve member wherein the sealing means is readilyaccessible for replacement and for selective adjustment of pressureabout the periphery of the seal means.

A further object of the invention is to disclose and provide a butterflytype valve means including actuating means for turning a valve memberand wherein the actuating means includes a simple effective camarrangement for turning a shaft connected to the valve member.

A still further object of the invention is to disclose and provide anactuator means as mentioned above wherein a double-headed fluid pressuremeans is used and dampening means are provided for cushioning andretarding movement of a piston head at the end of its stroke.

A still further object .of the invention is to disclose and provide abutterfly type valve means employing stub shafts for pivotally mountinga butterfly valve member and wherein bearing means of novel structuremount said stub shafts.

These and many other objects and advantages of the present inventionwill be readily apparent from the following description of the drawingsin which exemplary embodiments of the invention are shown.

In the drawings:

FIG. 1 is an elevational view of a valve means embodying the presentinvention, the elevation being partly in section and being taken in aplane transverse to the fluid passageway.

FIG. 2 is a transverse horizontal sectional view taken in the planeindicated by line IIII of FIG. 1.

FIG. 3 is a vertical sectional view taken in the plane indicated by lineIIIIII of FIG. 1.

FIG. 4 is an enlarged fragmentary sectional view taken in the same planeas that of FIG. 3 and showing the seal means of this invention.

FIG. 5 is a transverse sectional view taken in the plane indicated byline VV of FIG. 2.

FIG. 6 is an enlarged fragmentary vertical sectional view taken in aplane passing through and along the diameter of the fluid pressurecylinder actuating means and showing the construction of a piston head.

FIG. 7 is a fragmentary top plan view taken from the horizontal planeindicated by line VII-VII of FIG. 3.

FIG. 8 is a fragmentary enlarged sectional view showing the seal meansand valve member in valve open posi tion.

FIG. 9 is a fragmentary sectional view taken in a plane similar to theplane of FIG. 4 and showing a modification of the valve member.

FIG. 10 is a fragmentary side elevation partly in section of a modifiedvalve actuating means.

FIG. 11 is a horizontal sectional view taken in the plane indicated bythe line XIXI of FIG. 10.

One example of a fluid control valve means of butterfly type embodyingthis invention is generally indicated at 10 (FIG. 1). The valve means 10may comprise a compact, narrow or thin assembly adapted to be employedbetween flanged opposed ends 11 and 12 of conduit or pipe 13 and 14respectively adapted to conduct fluids of various characteristics. Theflanged ends 11 and 12 may be provided with suitably configured faces asat 15 and 16 respectively for providing a fluid-tight sealed connectionbetween the flanged pipe ends 11 and 12 and the valve means 10. Thefluid conducted in the pipes 13 and 14 may be gas or liquid under highor low pressures and at various temperature ranges. The construction andarrangement of valve means 10 is particularly adapted for use withfluids of cryogenic type, such as liquid hydrogen, liquid nitrogen, andthe like, having temperature ranges extending down to and in the rangeof minus 450 F.

The valve means 10 may generally comprise a valve body 20, a seal means21 carried by the body on the downstream side thereof (exemplary only),a valve member 22 having a construction designed for strength towithstand high pressures while providing maximum flow area when in openposition, pivotal mounting means 23 carried by the valve body for thevalve member and actuator means 24cooperably connected with the pivotalmounting means for opening and closing the valve member. In the example,the valve means is designed for open and shut operation; controlling ormodulating flow of fluid may be accomplished by the valve means ifdesired when used with fluids at normal temperature ranges and wherepressure drop across the valve means is not considered critical.

The valve body may comprise an annulus or annular member 26 having anexternal diameter approximately the same as the external diameter of theflanged ends 11 and 12, and having an internal diameter forming apassageway 27 approximately the same as the internal diameter of thepipes 13 and 14. Fluid may flow through passageway 27 in the directionas indicated in FIG. 3. Oppositely directed faces 28 and 29 of member 26may be configured to facilitate sealing of the joints at 15 and 16 withthe flanged ends 11 and 12. It should be noted that the member 26 isrelatively thin, that is, its dimension in an axial direction issubstantially less than its internal diameter. Member 26 may be made ofany suitable metal material depending upon the characteristics of thefluid with which it is to be used; for cryogenic fluids the member maybe made of stainless steel or the like.

Seal means 21 is carried by member 26 at one end of passageway 27 withinan annular enlarged recess 31 of selected configuration and extendingfrom the back face 29 of member 26. The seal means 21 may comprise anannular sealing member or ring 32 having a radially inwardly extendingsealing lip 33 for sealing contact in valve closed position as at 34with a curved peripheral edge face 35 on the valve member 22 as moreparticularly described hereafter. The sealing lip 33 extends from astepped or reduced recess 36 formed in the annular member 26. Thesealing element 32 includes a central cylindrical support portion 37disposed circumaxially with respect to the axis of the seal means, saidsupport portion 37 being integral with said lip 33 and with a radiallyoutwardly extending holding or securement portion 38 provided with anaxially directed annular rib 39 received within an annular groove 40 forholding and retaining the sealing ring 32 in the recess 36 on the valvebody 20. The holding portion 38 and rib 39 is covered and retained by agenerally L-section retaining or backing member 42, a radially extendingleg 43 of the member 42 serving to support and back the holding portion38 of the seal ring, while the generally axially extending leg 44 servesto underlie the cylindrical support portion 37 and to define an annularspace between edge face 45 on leg 44 and the opposed surface on themember 26 and through which the sealing lip 33 extends. Edge face 45limits displacement of the sealing lip 33 in an axial or downstreamdirection, while leg 44 limits radial inward displacement of the lip 33.

The sealing means 21 also includes an annular metal spring 47 which maybe held between the holding portion 38 and an annular rib defined byannular groove 40, said spring 47 having a radially inwardly and axiallyextending portion 47a bearing against sealing lip 33 at its radiallyoutermost surface. The spring 47 thus tends to bias the sealing lip 33radially inwardly, and movement of the sealing lip in an axial directionis limited and restrained by the opposed surfaces of the valve annularmember 26 and the edge face 45 of backing member 42.

The backing member 42 may be held in assembly with the sealing element32 and under selected adjustable circumferential pressure by means of apressure or retainer metal ring 50, said pressure ring 50 having athreaded connection with an annular member 26 as at 51 and beingprovided with a plurality of threaded circumferentially spaced bores 52in which a plurality of pressure set screws 53 may be threadedlyadjusted. Each set screw 53 may have pressure contact as at 54 with theback face of the backing member 42.

It will be readily apparent that uniform pressure may be applied to thebacking member 42 by pressure screws 53 .or pressure may be somewhatvaried at particular 10- cations along the member 42 so thatirregularities in metal surfaces, non uni-form sealing contact ofsealing lip 33 with the edge face 45, or locations where completesealing has not been effected may be subjected to variable additionalpressure in order to provide a zero leakage condition. In this respect,it should be noted from FIG. 4 that the backing member is provided aseat at 56 in a slightly indented annular sihoulder radially outwardlyof the groove 40. Since the pressure screws 53 contact the back face 54of the backing member radially inwardly of seat 56, pressure or momentforces may be imparted to selected locations along the backing memberwhich act to confine the sealing lip 33 between the edge face 45 and theopposed face of the valve body annular member. 'Phus movement of thesealing lip in an axial direction is further restrained and translated,because of the resilient material of the sealing lip, into a radialdirection for tighter sealing contact with the edge face 35 of the valvemember.

In this example, the valve member 22 is constructed for holding highpressure fluids when the valve member is in closed position. Valvemember 22 may comprise a pair of spaced parallel circular walls 60 ofselected thickness interconnected by a central diametrically disposedweb 61 lying generally perpendicular to the axis defined by stub shafts62 and 63. As best seen in FIG. 4, the web 61 has opposite concave faces65 smoothly merging with interior surfaces 66 of walls 60 and is fairedor tapered at its ends at 67 for minimizing interference with flow offluid passing through valve member through openings 68 when the valvemember is in open position. The openings 68 are further defined byrelatively thick metal sections 69 which are disposed transverse to theaxis of stub shafts 62 and 63 to provide sufficient metal for making aspl-ined connection for splined inner ends 7 0 and '71 respectively ofthe stub shafts 62 and 63. In FIG. '33, it may be noted that the splinedfaces on metal sections 69 may be formed by a single broaching operationthrough the valve member and a broaclhe'd opening 73 may be provided inthe web 61.

Edge face 35 of the valve member 22 may be formed as a spherical sectorof a sphere having a radius substantially equivalent to the radius ofthe internal surfaces of passageway 27. Edge face 35 may be providedwith a circumferential groove 75, including a convexly curved side wallsurface, spaced inwardly from the downstream face of disc wall 60.Sealing lip 33 contacts convex edge face 35 between groove 75 and thedownstream face of wall 60 so that when the valve member is movedbetween open and closed position wherein half the valve member passesbeneath the sealing lip 33 in a downstream direction and the other halfin an upstream direction, the sealing lip 33 will be smoothly guidedinto its ultimate sealing position over the convex curved groove sidewall surfaces and the edge face 35. If desired, such a groove 75 may beprovided along the circumferential edge portion adjacent the upstreamwall 60 so that the valve member may be reversed and used withoutdesignating an upstream or downstream. side of the valve member.

It is important to note that while the spherical radius of edge face 35on the valve member is substantially the same as the radius of theinternal faces of the passageway 27, the internal radius of the internaledge of sealing lip 33 is somewhat less than the radius of thepassageway 27 and edge face 35. A transverse plane passed through thesealing line of contact of sealing lip 33 with the edge face 35 wouldshow such line of contact to be of a radius somewhat greater than theradius of the circle defining the downstream face of wall 60. Theserelationships are important because the valve member 22 with an axis Vindicated as lying in a plane passing through the valve member midwaybetween walls 60 lies in offset or eccentric relation to the axis S ofthe stub shafts 62 and 63. In this example the axis S is displacedupstream and sidewise from the axis V and at an angle not greater thanapproximately 45 as measured from a plane passing longitudinally throughthe passageway 27 and axis S. Thus when the valve member is turned 90 toopen position from closed position in which the sealing lip 33 has tightand complete sealing contact with the edge face 35, the edge face 35 andthe valve member will be shifted or displaced slightly upstream so thatsealing lip 33 now lying transverse to edge face 35 is free from contactwith the edge face 35. This relationship is best seen in FIG. 8.

The importance of this relationship of the seal means 32 with the valvemember in open position will be more apparent when one considers that invalve open position a cryogenic fluid is passing through the valvepassageway 27 and the sealing member 32 is immersed in a fluid having atemperature ranging to minus 450 F. or the like. The material of sealingmember 32 which may preferably be a filled Teflon material will becomevirtually hard and rigid at such temperatures. In the event the sealinglip 33 was in contact with the edge face 35 in open position,indentations or impressions made by edges of face 35 at diametricallyopposite areas on the sealing ring 32 would be formed and madetemporarily permanent. Under such condition when the valve member wasmoved to closed position, two leakage zones would have been formed andsuch leakage would not be stopped until the Teflon material of thesealing ring 32 had returned to higher temperatures at which it becamerel-atively flexible, compliant and resilient and returned to itsoriginal shape. Thus by offsetting the axis V of the valve member andthe shaft axis S, by forming the edge face 35 of the valve member as aspherical sector, and by displacing the valve member slightly sidewardlyforwardly or upstream, in this example, the sealing edge 33 of the sealmember will be in proximate but spaced free relation from edge face 35when the valve member is in open position.

Means for pivotally mounting the valve member 22 include the stub shafts62 and 63 and the splined connections 70 and 71 with the valve member aspreviously described. Valve shaft-s 62 and 63 may be mounted in bearingmeans 77 provided in diametrically :opposite bores 78 formed in theannulus 26. Since the bear-ing means for each stub shaft may be the samelike reference numerals 'will be used in the description thereof.

Each stub shaft may be provided with an annular groove 79 carrying ametal retaining and shaft thrust ring 80. Inwardly of ring 80 may beprovided a circular seal element 81 for sealing the outer end of thesplined portion of the stub shaft. In this example each stub shaft maybe received Within a filled Teflon frustoconical bearing element 82having an outer conical surface which corresponds with an internalconical surface 83 provided in the bore 78. The element 82 is retainedunder axial or thrust pressure for tight sealing engagement with theshaft and with adjacent surfaces of the bore by a pressure ring 84 and aplurality of circumferentially spaced pressure screws 85 carried by acollar 86 held in selected axial relation with respect to the shaft by alock and sealing member 87 seated in an internal groove 88 provided onthe internal surfaces of bore 78. A spacer block 90 provided with innerand outer circumferential grooves containing Teflon seal rings 91 and 92and seated against v a shoulder 93 mayprovide outer seal means for thestub shaft. Stub shaft 62 may terminate in an exterior end housing 94which may be provided with a conduit connection at 95 for means (notshown) to determine the position of shaft 62. The spacer block 90 mayalso be provided with a vent port 96 which communicates with the spacebetween the block 90 and the pressure support collar 86.

The seal means for stub shaft 63 is identical to that described abovefor stub shaft 62. Stub shaft 63, however, includes an extension 100which projects into actuator means 24.

Actuator means 24 may be provided at the top of the valve body 26 andmay extend transverse to the axis of the body 26. Actuator means 24serves to turn the valve member 22 through 90 from closed to openposition and vice versa. Actuator means 24 may be operated by suitablepressure fluid and may be controlled so as to cause relatively slowopening of the valve member; for exam ple, an opening period of time maybe about five seconds and a relatively rapid closing period of about 500milliseconds.

The actuator means 24 may comprise a housing means 102 includinghorizontally split top and bottom center housing portions 103 and 104and cylindrical end portions 105 each of the same construction. Thecenter housing portions 103 and 104 may be secured together as by spacedstud bolts 106. A suitable recess 107 may be provided in portion 104 forreceiving and connecting the spacer block 90, forming part of the shaftseal means for stub shaft 63 with the housing means. The portions 103and 104 each contain a bearing means 108 adapted to rotatably mount theshaft extension 100. The top bearing means 108 may be retained inposition by a bearing cap 109 provided with a seal ring 110 and retainedby a stud screw 111 having threaded engagement with the top end of shaftextension 100. I

Opposed faces of the housing portions 103 and 104- may be suitablymilled and shaped to provide a pair of parallel longitudinally extendingWays 113 and 114 adapted to slidably receive and mount an actuator platemember 115 of generally rectangular plan and of relatively heavy metalsection. Plate 115 is provided with a central longitudinally extendingslot 116 through which the shaft extension 100 extends. An opening 117is provided centrally along one side wall of slot 116 for receiving aroller 118 carried at a yoke-like end of arm 119 having its opposite endfixedly connected to the shaft extension 100 as by a spline connection120. Roller 118 is carried on pivot pin 121 and the edge of roller 118has clearance from an arcuate face 122 formed in housing portions 103and 104. The arcuate face 122 is formed on a radius having the shaftextension as its center and may be transversely concave as seen in FIG.3.

The plate 115 may carry at each end a circular piston head 124 eachbeing carried on a longitudinally extending boss 125 provided on plate115. Each piston head 124 may comprise an outer piston Wall 126, aninner piston Wall 127, and a piston ring member 128 carried on outercircumferential faces of the piston walls 126 and 127. The piston head124 is held in assembled relation with the plate 115 by a plurality ofstud screWs 130 threaded as at 131 in the end face of plate 115.

Suitable seals may be provided at 132 between the boss 125 and the innerpiston Wall 127, at 133 for sealing each stud screw 130, at 134 betweenthe juncture of the inner faces of the ring 128 and piston walls 126 and127, and at 135 between the circumferential end face of the ring 128 andthe internal cylindrical surfaces 136 of the cylindrical end portions105. It should be noted that piston wall 126 is slightly spaced as at138 from piston Wall 127 and is also provided with a port 139 forcommunication between space 138 and chamber 164.

It should also be noted that circumferential edge faces of the pistonwalls 126 and 127 are oppositely inclined to form a shallow V as at 140and that the internal circumferential face of the piston ring member 128is provided with a V-shape configuration to correspond to the V-shape140.

Each cylindrical end portion 105 may comprise a cylindrical wall 150having at its inner end a circumferential rib 151 for interlockingengagement with the housing portions 103 and 104. Adjacent its outerend, wall 150 may be provided with external threads for threadedengagement as at 152 with a cylinder head 153. The cylinder head 153 maybe provided with an internal groove 154 carrying a seal ring 155 forsealing engagement with the outer end portion of wall 150. On end wall156 of the cylinder head 153 may be provided an annular inwardlyextending stop rib 157 against which a piston wall 126 may abut as at158. End wall 156 may be provided with a threaded port 159 for a fitting160 for connecting a fluid pressure line 161 thereto. A lock ring 162may also be threaded on the external threads 152. Thus at opposite endsof the actuator housing means 102 are provided chambers 164 for suitableactuating pressure fluid such as air or liquid.

Operation of the actuator means 24 may be best understood from aconsideration of FIG. 2. As pressure fluid is introduced to the leftchamber 164 the piston head 124 will be driven to the right and willcause the plate 115 to move to the right. As plate 115 moves, the roller118 is caused to follow the plate 115 and the linear motion of the plate115 is translated through the roller 118 and arm 119 into turning orrotational movement of the shaft extension 100. The arm 119 will swingthrough a are as indicated in FIG. 2 and at such final position theright piston head 124 is in abutment against the stop rib 157 on theopposite piston cylinder head 153. It should be noted that as the rightpiston head 124 approaches the cylinder head wall 156, fluid in theright chamber 164 is evacuated through the pipe 161. However a certainamount of fluid pressure is existent in the progressively reduced volumeof the chamber 164 and fluid under such pressure is limitedlycommunicated through port 139 in outer piston Wall 126 to the space 138between the piston walls. Upon contact of piston wall 126 with stop rib157 piston wall 127 moves towards wall 126 tending to compress fluid inspace 138 and effecting some fluid damping movement (dependent upon thecharacteristics of the fluid) of the piston head at that end of itsstroke. After contact of piston wall 126 with stop rib 157 thefrictional resistances at the contacts of the inclined circumferentialedge faces of walls 126 and 127 with the piston ring member 128 coactwith the ring-spring action of ring member 128 and cylinder surfaces 136to frictionally absorb and dissipate energy and to produce a shockabsorbing action which does not adversely influence the accuracy offinal valve positioning in either open or closed position. Due to theV-configuration at of the circumferential edge faces of piston walls 126and 127, the moving together of said walls 126, 127 tends to impart asby a wedging action is radially directed force against the piston ringmember 128 and causes the piston ring member 128 to also frictionallyengage internal surfaces 136. Thus as the volume of the right chamber164 is reduced to its minimum and as the piston head 124 reaches the endof stroke a primary frictional damping action is imparted to the pistonhead 124.

As the valve member 22 is turned between open and closed position by theactuator means 24 as above described, it will be readily apparent thatthe sealing lip 33 and the valve member 22 change their relativepositions so that when the valve member 22 is in open position thesealing lip will be out of contact with the edge face of the valvemember as above described. In such open position the openings 68provided in the valve member provide maximum fluid flow through thepassageway 27 so that pressure drop through the valve means is reducedto a minimum. It will also be understood that in closed position ofvalve member 22 the beam type or girder type construction of the valvemember will be subjected to substantial fluid pressure and in view ofits beam-like construction, the valve member is capable of withstandingsuch pressure without substantial deflection as in bending. In view ofthe structural strength and rigidity of the valve member 22 it will bereadily apparent that the transmission of such deflection and bendingforces to the bearing means is also reduced to a minimum because of thesplined stub shaft connections at relatively heavy metal sections of thevalve member.

It should be noted that at the very low temperatures for which thisvalve means is designed to operate any contraction of the parts of thevalve because of such low temperature will tend to increase the sealingeifect at sealing lip 33 because as sealing lip 33 contracts it will beurged into tighter sealing engagement with the edge face 35 because ofits dimensional change in response to decreasing temperatures or lowertemperatures than those at which the valve was assembled with a presetsealing pressure. Similarly, the spring 47, because of its presetcircumferential loading at the time of assembly, will respond to adecrease in temperature by contraction to assist and maintain a tightseal. Upon increase in temperature the ring 47 and the sealing ring willrespond thereto by relieving sealing pressure until the preset sealingload is reached. Likewise the fluid pressure forces acting against thevalve member 22 in a downstream direction which may result in anystresses or minute downstream displacement of the rigid valve memberalso tends to press the edge face 35 more tightly against the seal means33. Thus the valve member 22 which has a high section modulus is capableof resisting loads due to fluid pressures of large magnitude andtransfers such loads to the stud shafts while minimizing deflection ofthe valve disc because of these loads.

The construction of valve means 20 should be particularly noted withrespect to the ease of assembly in a fluid pipe line such as 13 and 14and also the ease of disassembly and ready access of the seal means forreplacement or adjustment thereof if desired. Since the seal means islocated on the downstream side of the valve member and with the valvemember in close position it will be readily apparent that the pressureset screws 53 may be readily adjusted after pipe 14 is disconnected. Theretaining ring 50 may be removed if desired and the support ring 42 maybe then readily lifted away and out of the recess in the annular valvebody member to replace the seal means 32 is necessary while the valvemember is in closed position.

A modification of the construction of the valve member is shown in FIG.9 in which a valve means embodying this invention is designed for use ininstallations Where fluid pressures do not require a valve member of thebeam or grider type construction described in the prior embodiment. InFIG. 9 the valve member 200 may comprise a single wall 201 spaced fromthe axis of rotation provided by the stub shafts 202 and 203. The valvewall 201 may be provided with diametrically opposed lug extensions 204provided with openings 205 in which may be received inner ends 206 ofstub shafts 202 and 203. Each shaft may be secured as by a pin 207. Theends of the lugs 204 remote from the wall 201 may be provided with asuitable outer curved face 208 having a diameter such that when thevalve member 200 is rotated through 90 the face 208 will be free ofcontact with the seal means 209.

The seal means 209 may be of a different shape and configuration thanthat of the prior embodiment but it will be noted that it includes asealing lip 210 biased radially inwardly against the sealing edge face211 provided on the circumference of the valve Wall 201. The seal means209 may be formed of generally L or V section so disposed that the innerleg 212 of the seal means extends radially inwardly and axially. Thuswhile the general structure and shape of the seal means 200 is somewhatdifferent. than that shown in the prior embodiment its relation andfunction with respect to the valve member 200 is substantially the sameas the prior embodiment.

In FIGS. and 11 is illustrated a modification of the actuator means 24.A shaft extension 63 may be of substantially greater length than thestub shafts previously shown may be enclosed within an outer elongatedcylindrical housing 220 having an internal chamber 221 in Which anyfluid escaping through seals between the stub shaft 63' and the housing220 and the annular valve body member may vaporize to gas which mayserve as a heat barrier and thus provide a vapor pressure chambercontaining a relatively Warm gas (instead of cryogenic fluid) andserving to assist in sealing stub shaft 63. The shaft housing 220 mayterminate in a top mounting flange 222 for the actuator means 24.

The actuator means 24 operates in virtually the same manner as the priorembodiment and only those differences in structure and operation will bedescribed. Actuator means 24 includes an actuator housing 102' which maybe mounted on the flange 222 in suitable manner. The stub shaft 63' isprovided a splined connection at 120' with a cam member or arm means119' said arm means 119' comprising a central hub 224 and spaced top andbottom arm plates 225 interconnected thereby. The spaced plates 225carry a pivot pin 121 for supporting a cam roller 118' therebetween. Thecam roller 118 is contained within .an opening 117 associated withelongated central slot 116 provided in a piston plate The slot 116'receives therewithin the extension of shaft 63 and plate 115 carries atits opposite ends piston heads 124' operable in piston chambers 164. Theextension of shaft 63' may be further projected upwardly beyond thesplined connection at to provide a connection with switch means (notshown).

The actuator means 24 is operable in similar manner to the priorembodiment and as the piston plate 115 moves to the left as viewed inFIG. 11 the roller 118' will translate such motion through the arm means119 to the stub shaft extension 63 to cause rotation thereof.

It will be apparent to those skilled in the art that the actuator meansof the last embodiment shown in FIGS. 10 .and 11 provides means fordeveloping a pressure in pressure chamber 221 for assisting in the sealof the stub shaft 63 and that such stub shaft may be readily turned inaccordance with desired opening and closing requirements by the mannerin which pressure fluid is introduced into the piston chambers 164 as inthe prior embodiment. Such pressurized seal may also be employed in theprior embodiment.

It will be understood that various modifications and changes may be madein the valve means of this invention which comes within the spirit ofthe invention and all such changes and modifications coming within thescope of the appended claims are embraced thereby.

I claim:

1. A seal means for a valve means including a stationary valve bodyhaving a passageway for fluid and a movable valve member adapted toclose said passageway, comprising: recess means in the valve bodyopening toward said passageway; a sealing ring member having L-shapedcross section providing a radially inwardly directed sealing portionextending into said passageway and an annular support portion for saidsealing portion, said support and sealing portions being radiallyinwardly movable, and spring means carried by said valve body forapplying radially inwardly directed pressure to said support portionabove said sealing portion for urging said sealing portion toward saidpassageway, said spring means comprising a metal responsive totemperature decreases for thermally augmenting selected sealingpressure.

2. A seal means for a valve means including a stationary valve bodyhaving a passageway for fluid and a movable valve member adapted toclose said passageway, comprising: recess means in the valve body; asealing ring member having L-shaped cross section providing a radiallyinwardly extending sealing portion and an annular support portion forsaid sealing portion, said support portion and sealing portion beingradially inwardly movable, and Vi]. spring means within said recessmeans exerting on said support portion a selected predetermined radiallyinwardly directed pressure at a normal temperature and having acontraction characteristic greater than the material of the valve memberin decreasing temperature ranges for augmenting sealing pressure.

3. A seal means for cryogenic fluids responsive to selected physical andtemperature conditions of fluid, comprising a body member; a recessmeans on said body; and seal means within the recess means comprising asealing ring member having a radially extending sealing portion, asupport section for said sealing portion angularly related to saidsealing portion, and a temperature responsive biasing means in saidrecess means and cooperable with said support section for imparting aradially directed force to said sealing portion in response to changesin temperature.

4. A seal means responsive to physical and temperature changes in afluid, comprising a body member providing an elongated passageway forfluid and having an ann-ular recess means; and a sealing ring member ofL-cross section Within the recess means and including a sealing portionextending radially in to said passageway; and

spring member bearing against said ring member adjacent to said sealingportion for imparting a radially directed seal force to said sealingportion, said spring member having a response to temperature changes foraugmenting said radially directed seal force.

5. A seal means for a pair of body members arranged in coaxialconcentric relation comprising a recess means on the outerconcentrically arranged body member; and a seal means mounted in saidrecess means and having a radially inwardly extending sealing portion,said seal means including a radially outwardly and axially extendingsection, and a spring member bearing against said section for urgingsaid sealing portion radially inwardly and thermally responsive toaugment sealing pressures upon decrease in temperature.

6. A seal construction for cryogenic fluids and responsive totemperature changes comprising in combination a body member having aninternal cylindrical surface; re-

cess means on said body member; a sea-l means positioned Within saidrecess means and comprising a non-metallic sealing member having aradially inwardly directed sealing portion having a bead-like sealingedge, and means coacting with said radially inwardly directed sealingportion to effect an augmented sealing pressure force and including ametallic thermally responsive ring member having pressure engagement'with the sealing portion at locations radially outwardly of the saidseal-ing edge to impart radially inwardly directed force components tosaid bead-like sealing edge, and a backing member having an annularportion supporting said sealing portion against axial displacementcaused by fluid pressure against said sealing portion.

7. A temperature responsive seal construction comprising in combination:a body member provided with a passageway for fluid and having an axis;recess means in the body member facing said axis and passageway; asealing member of non-metallic material within said recess means andhaving a sealing portion directed toward said axis in a plane normal tosaid axis; said sealing member having a section extending away from saidsealing portion and providing a spring seating surface; a spring memberseated on said seating surface and biasing said sealing portion towardsaid axis with a selected initial pressure and thermally responsive tochanges in temperature to augment said sealing pressure; a backingmember holding said sealing member in said recess means and supportingsaid sealing portion against axial movement; a retaining member carriedby said body member in spaced relation to said backing member; and aplurality of pressure members mounted on said retaining member andhaving pressure engagement with said backing member for uniformlyloading said backing member and sealing member.

8. A thermally responsive seal construction comprising in combination: abody member provided with a fluid passageway along an axis of said bodymember; recess means in said body member facing said axis; a sealingring member in said recess including a generally L-section having asealing portion of relatively thick section directed toward said axis ina plane normal to said axis; said L-section including a portionextending in the direction of said axis and providing a spring seatingsurface; an annular spring member seated on said seating surface andbiasing said sealing portion toward said axis with a selected initialpressure and thermally responsive to changes in temperature to augmentsaid sealing pressure; an L-shaped backing member supporting saidsealing member and having an axially directed backing portion limitingaxial movement of said sealing portion on the sealing member; aretaining ring carried by the body member; and pressure means carried bythe retaining ring and having pressure engagement with the backingmember for loading said backing member and sealing member.

9. A seal construction as stated in claim 8 wherein said spring seatingsurface is radially opposite said sealing portion.

References Cited by the Examiner UNITED STATES PATENTS 1,488,296 3/ 1924Stevens 251174 1,489,857 4/ 1924 Stevens 251174 2,680,592 6/ 1954 Zierer251305 2,892,609 6/ 1959 Bi-bbo 25 1-175 X 2,893,682 7/ 1959 Hintzman251173 2,974,921 3/1961 Kaswan 251306 X 2,988,320 6/ 1961 Kent 2511743,013,769 12/1961 Volpin 251174 3,049,335 8/1962 Daumy 251305 3,077,9022/1963 Vickery 251174 X 3,127,182 3/1964 Wardleigh 251306 X 3,144,0408/1964 White 251307 X FOREIGN PATENTS 1,251,575 12/ 1960 France.

654,449 6/1951 Great Britain.

697,113 10/ 1953 Great Britain.

903,802 8/ 1962 Great Britain.

'ISADOR WEIL, Primary Examiner.

CLARENCE GORDON, Examiner.

1. A SEAL MEANS FOR A VALVE MEANS INCLUDING A STATIONARY VALVE BODYHAVING A PASSAGEWAY FOR FLUID AND A MOVABLE VALVE MEMBER ADAPTED TOCLOSE SAID PASSAGEWAY, COMPRISING: RECESS MEANS IN THE VALVE BODYOPENING TOWARD SAID PASSAGEWAY; A SEALING RING MEMBER HAVING L-SHAPEDCROSS SECTION PROVIDING A RADIALLY INWARDLY DIRECTED SEALING PORTIONEXTENDING INTO SAID PASSAGEWAY AND AN ANNULAR SUPPORT PORTION FOR SAIDSEALING PORTION, SAID SUPPORT AND SEALING PORTIONS BEING RADIALLYINWARDLY MOVABLE, AND SPRING MEANS CARRIED BY SAID VALVE BODY FORAPPLYING RADIALLY INWARDLY DIRECTED PRESSURE TO SAID SUPPORT PORTIONABOVE SAID SEALING PORTION FOR URGING SAID SEALING PORTION TOWARD SAIDPASSAGEWAY, SAID SPRING MEANS COMPRISING A METAL RESPONSIVE TOTEMPERATURE DECREASES FOR THERMALLY AUGMENTING SELECTED SEALINGPRESSURE.